DE4339305A1 - Solenoid valve for hydraulic brake system with feedback control - Google Patents

Solenoid valve for hydraulic brake system with feedback control

Info

Publication number
DE4339305A1
DE4339305A1 DE4339305A DE4339305A DE4339305A1 DE 4339305 A1 DE4339305 A1 DE 4339305A1 DE 4339305 A DE4339305 A DE 4339305A DE 4339305 A DE4339305 A DE 4339305A DE 4339305 A1 DE4339305 A1 DE 4339305A1
Authority
DE
Germany
Prior art keywords
valve
solenoid valve
pressure
channel
pressure medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
DE4339305A
Other languages
German (de)
Inventor
Peter Dr Ing Volz
Dalibor Zaviska
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
ITT Automotive Europe GmbH
Alfred Teves GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Priority to DE4339305A priority Critical patent/DE4339305A1/en
Priority to JP51418595A priority patent/JP3735659B2/en
Priority to DE59408551T priority patent/DE59408551D1/en
Priority to EP95900111A priority patent/EP0728085B1/en
Priority to ES95900111T priority patent/ES2134428T3/en
Priority to US08/464,902 priority patent/US5647644A/en
Priority to CZ951816A priority patent/CZ181695A3/en
Priority to SK966-95A priority patent/SK96695A3/en
Priority to PCT/EP1994/003622 priority patent/WO1995013945A1/en
Publication of DE4339305A1 publication Critical patent/DE4339305A1/en
Priority to KR1019950702900A priority patent/KR960700167A/en
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4275—Pump-back systems
    • B60T8/4291—Pump-back systems having means to reduce or eliminate pedal kick-back
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • B60T8/5037—Pressure reapplication using restrictions in hydraulic brake systems closed systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/02—Brake control by pressure comparison
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/90—ABS throttle control

Abstract

Hydraulic fluid flow to a valve seat (116) enters the valve through a restricted opening (130), into the intermediate space (117) of the piston (8), via a further restricted passage (129), partially converting the pressure energy at the restriction (130) into kinetic energy. The valve seat is opened and closed by an electromagnetically operated slider (11). Under normal braking conditions, the hydraulic pressure is insufficient to compress the spring (7) and the pressure is transmitted to the brake through channel (3). With excess pressure applied the piston (8) closes against the seal (115), shutting off the flow through the hole (116). Flow is restored by operation of the solenoid and hence lifting of the slider.

Description

Die Erfindung betrifft ein Elektromagnetventil, insbesonde­ re für hydraulische Bremsanlagen mit Schlupfregelung nach dem Oberbegriff des Anspruchs 1 und stellt eine weitere Ausgestaltung des Gegenstandes der Erfindung nach Patent . . . (Patentanmeldung: Aktenzeichen P 43 19 227.0) dar.The invention relates to an electromagnetic valve, in particular right for hydraulic brake systems with slip control the preamble of claim 1 and represents another Design of the subject of the invention according to a patent . . . (Patent application: file number P 43 19 227.0).

Die diskontinuierliche Druckmittelsteuerung bei schlupfge­ regelten Bremsanlagen mittels digital schaltbaren Ein­ laß- und Auslaßventilen führt infolge des impulsartigen Druckverlaufs zur unerwünschten Schallemission.The discontinuous pressure medium control at schlupfge controlled braking systems using digitally switchable on Let and exhaust valves result from the pulse-like Pressure curve for undesirable noise emission.

Bei der in der Hauptanmeldung beschriebenen Bremsanlagen hat es sich gezeigt, daß die vorgeschlagenen Lösungen zur Anordnung des mit der schaltbaren Blende versehenen Ring­ kolbens im Einlaßventil, ein ungewolltes Schalten des Ring­ kolbens in die Blendenstellung bei manueller, schlupffreier Bremsbetätigung nicht immer vermieden werden kann. Insbe­ sondere bei schneller Betätigung der Bremse (Panikbremsung) kann nicht mit hinreichender Sicherheit eine unerwünschte vorzeitige Aktivierung der dem Einlaßventil zugeordneten schaltbaren Blende ausgeschlossen werden, so daß das Pedal­ gefühl und der fahrzeugspezifische Druckaufbaugradient ver­ ändert wird. Eine durch die Blendenwirkung hervorgerufene Verringerung des Druckaufbaugradienten führt zwangsläufig zu einer Minderung der Bremsleistung. In the brake systems described in the main application it has been shown that the proposed solutions for Arrangement of the ring provided with the switchable cover piston in the inlet valve, an unwanted switching of the ring piston in the aperture position with manual, slip-free Brake actuation cannot always be avoided. In particular especially when the brake is applied quickly (panic braking) cannot with reasonable certainty be an undesirable early activation of those assigned to the inlet valve switchable aperture can be excluded, so that the pedal feeling and the vehicle-specific pressure build-up gradient ver will change. A caused by the aperture effect Reducing the pressure build-up gradient leads inevitably to a reduction in braking performance.  

Deshalb wurde in der Patentanmeldung P 43 32 819.9 vorge­ schlagen, stromaufwärts bzw. stromabwärts zum Elektro­ magnetventil (Einlaßventil) zusätzlich Festblenden anzuord­ nen, jedoch mit dem Ergebnis, daß der Umschaltdruck, bzw. die Schaltdruckdifferenz der schaltbaren Blende relativ hoch bleibt, was während der Bremsdruckregelung zu uner­ wünschten Volumenstromschwankungen führen kann.Therefore, it was featured in patent application P 43 32 819.9 beat, upstream or downstream to the electro solenoid valve (inlet valve) to arrange additional orifices NEN, but with the result that the switching pressure, or the switching pressure difference of the switchable orifice relative remains high, which is too important during brake pressure control desired flow fluctuations can lead.

Daher ist es die Aufgabe der Erfindung, unter Beibehaltung eines möglichst unveränderten einfachen Aufbaus, der aus der Hauptanmeldung hervorgegangenen Bremsanlage, einen Lö­ sungsweg aufzuzeigen, der ein vorzeitiges, unerwünschtes Aktivieren der schaltbaren Blende in der schlupffreien Nor­ malbremsphase verhindert.Therefore, it is the object of the invention while maintaining of a simple structure that remains as unchanged as possible brake application, a Lö way of showing a premature, undesirable Activate the switchable shutter in the non-slip Nor Malbremsphase prevented.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnen­ den Merkmale des Patentanspruchs 1 gelöst, wonach ein stromaufwärts zum Ventilsitz angeordneter Druckmittelkanal eine Querschnittsverengung aufweist, in die eine in Rich­ tung einer Stirnfläche des Ringkolbens sich erstreckende Kanalabzweigung geringer Nennweite einmündet, wodurch die Druckenergie der in das Elektromagnetventil einströmenden Druckmittelsäule in der Querschnittsverengung in kinetische Energie umgesetzt ist, die in der Kanalabzweigung ein Druckgefälle initiiert.According to the invention, this object is characterized by the solved the features of claim 1, after which Pressure medium channel arranged upstream of the valve seat has a cross-sectional constriction into which one in Rich tion of an end face of the annular piston extending Duct branching of small nominal diameter opens, whereby the Pressure energy of the flowing into the solenoid valve Pressure medium column in the cross-sectional constriction in kinetic Energy is implemented in the channel junction Pressure drop initiated.

Durch die erfindungsgemäße Konstruktion wird das unmittel­ bar am engsten Strömungsquerschnitt entstehende Druckgefäl­ le zum Halten des Ringkolbens in der deaktivierten Schalt­ stellung genutzt, um das vorzeitige Schalten des Ringkol­ bens in die Blendenstellung während einer schlupffreien Normalbremsung zu verhindern. Due to the construction according to the invention, the immediate bar at the narrowest flow cross-section le for holding the ring piston in the deactivated switch position used to switch the ring piston bens in the aperture position during a slip-free To prevent normal braking.  

Weitere Merkmale, Vorteile und Anwendungsmöglichkeiten der Erfindung gehen aus der nachfolgenden Beschreibung mehrerer Ausführungsbeispiele hervor.Other features, advantages and possible uses of the Invention will emerge from the following description of several Embodiments emerge.

Es zeigen:Show it:

Fig. 1 eine Teilansicht eines elektromagnetischen Einlaß­ ventils in vergrößerter Darstellung, mit der er­ findungsgemäßen Kanalanordnung unterhalb des Ven­ tilschließgliedes, Fig. 1 is a partial view of an electromagnetic inlet valve in enlarged representation, with which he tilschließgliedes inventive channel arrangement below the Ven

Fig. 2 eine weitere alternative Ausführungsform von Ein­ zelheiten innerhalb des Einlaßventils. Fig. 2 shows a further alternative embodiment of a details within the intake valve.

Die Fig. 1 zeigt ein konstruktives Ausführungsbeispiel zum Gesamtaufbau des Einlaßventils 1 für eine schlupfgeregelte Bremsanlage im Längsschnitt. Das Einlaßventil 1 weist einen Ventilträger 10 auf, der das Ventilschließglied 11 und die Kanalführung der vom Bremsdruckgeber 5 und der Hilfsdruck­ pumpe 18 kommenden Hauptdruckleitung 2 beinhaltet. Der Ven­ tilträger 10 ist vorzugsweise in Patronenbauweise (Ein­ schraubpatrone, Verstemmpatrone, Patrone mit Spreizring) in einem Ventilaufnahmekörper 9 integriert. In der gewählten Darstellung des Ventilbefestigungssystems ist der Ventil­ träger 10 mittels einer zweifachen Selbstverstemmung im Ventilaufnahmekörper 9 befestigt. Die Abdichtung des Ven­ tilträgers 10 im Ventilaufnahmekörper 9 ist durch die Selbstverstemmung gewährleistet. Es besteht eine Druckmit­ telverbindung über die Hauptdruckleitung 2, die am Brems­ druckgeber 5 und der Hilfsdruckpumpe 18 angeschlossen ist, durch einen am Fortsatz des Ventilträgers 10 aufgeclipsten Plattenfilter 21 und über das in der Grundstellung offen geschaltete Ventilschließglied 11 zum Ringkolben 8. Von dort gelangt Druckmittel über den offenen Ringspalt am Magnetkern 127 sowie auch im geringen Umfang über die Blen­ de 4 in Richtung des dem Anschluß zur Radbremse 3 vorge­ schalteten Ringfilters 22. Am Magnetkern 127 steht eine Ventilhülse über, auf die eine in der Abbildung nicht ex­ plizit dargestellte Ventilspule gestülpt ist. Die Ventil­ hülse bildet mit dem Magnetkern eine im Ventilträger 10 verstemmte Einheit. Ein mit einem Magnetanker versehener Ventilstößel ragt durch den Magnetkern 127 bis zum Ventil­ sitz 116 und bildet am Endbereich das Ventilschließglied 11. Fig. 1 shows a constructive embodiment of the overall structure of the inlet valve 1 for a slip-controlled brake system in longitudinal section. The inlet valve 1 has a valve carrier 10 , which includes the valve closing member 11 and the channel guide of the brake pressure sensor 5 and the auxiliary pressure pump 18 coming main pressure line 2 . The Ven tilträger 10 is preferably integrated in a cartridge design (a screw cartridge, caulking cartridge, cartridge with expansion ring) in a valve receiving body 9 . In the selected representation of the valve fastening system, the valve carrier 10 is fastened in the valve receiving body 9 by means of double self-restraint. The sealing of the Ven tilträger 10 in the valve receiving body 9 is ensured by the self-caulking. There is a Druckmit telverbindung over the main pressure line 2 , which is connected to the brake pressure transmitter 5 and the auxiliary pressure pump 18 , by a clipped on the extension of the valve carrier 10 plate filter 21 and via the valve closing member 11 open in the basic position to the annular piston 8th From there, pressure medium passes through the open annular gap on the magnetic core 127 and also to a small extent via the Blen de 4 in the direction of the ring filter 22 connected upstream to the connection to the wheel brake 3 . At the magnetic core 127 there is a valve sleeve on which a valve coil, not shown explicitly in the figure, is put. The valve sleeve forms a caulked unit in the valve carrier 10 with the magnetic core. A valve tappet provided with a magnet armature projects through the magnetic core 127 to the valve seat 116 and forms the valve closing member 11 at the end region.

Der Ringkolben 8 übernimmt infolge einer Querbohrung in der Ringkolbenwandung die schaltbare Blendenfunktion. Dieser ist auf dem Fortsatz des den Ventilsitz 116 aufweisenden rotationssymmetrischen Zentralkörpers 114 im Ringraum 126 axial beweglich geführt. Der Ringkolben 8 stützt sich unter Wirkung einer Druckfeder 7 mit seinem als Anschlag wirksa­ men äußeren Bund 119 an der Bohrungsstufe des Ringraums 126 im Ventilträger 10 ab. Der Ringkolben 8 weist im wesent­ lichen die Form einer Hülse auf, die an ihrer dem Magnet­ kern 127 zugewandten Stirnfläche den mit einem Gummidicht­ sitz 115 versehenen Stirnbereich des Magnetkerns 127 gegen­ überliegt. Bei Wunsch oder Bedarf kann die Abdichtung auch als metallische Flachdichtung oder mit einem im Stirn­ flächenbereich des Ringkolbens 8 eingefaßten O-Ring ausge­ führt sein.The annular piston 8 takes over the switchable diaphragm function as a result of a transverse bore in the annular piston wall. This is guided axially movably in the annular space 126 on the extension of the rotationally symmetrical central body 114 having the valve seat 116 . The annular piston 8 is supported under the action of a compression spring 7 with its outer collar 119 , which acts as a stop, on the bore step of the annular space 126 in the valve carrier 10 . The annular piston 8 has in the union Wesent the form of a sleeve which at its core the magnet 127 facing the end face with a rubber seal seat 115 end region provided the magnetic core 127 is opposite. If desired or required, the seal can also be carried out as a metallic flat gasket or with an O-ring bordered in the end face area of the annular piston 8 .

Auf der vom Magnetkern 127 abgewandten Stirnseite des Ring­ kolbens 8 befindet sich im Zwischenraum 117 ein Dichtring 124, der ein Überströmen von Druckmittel vom Bremsdruckge­ ber 5 in Richtung der Radbremse 3 verhindert. On the end of the ring piston 8 facing away from the magnetic core 127, there is a sealing ring 124 in the intermediate space 117 , which prevents overflow of pressure medium from the Bremsdruckge via 5 in the direction of the wheel brake 3 .

Der Zwischenraum 117 steht über eine Kanalabzweigung 129, die sich zwischen dem Zentralkörper 114 und dem Ventilträ­ ger 10 erstreckt, mit einer im unteren Bereich des Zentral­ körpers 114 vorgesehenen Querschnittsverengung 130 in Ver­ bindung, die vorzugsweise durch einen Blendeneinsatz 131 entstanden ist. Der sich mit seinem Fortsatz in den Innen­ raum des Ventils erstreckende rotationssymmetrische Zen­ tralkörper 114 ist in die Stufenbohrung des Ventilträgers 10 eingepreßt bzw. verstemmt. In der gezeigten Ausführungs­ form ist der Ventilsitz 116 als integrales Bestandteil der koaxial zum Ventilschließglied 11 verlaufenden Bohrung des Zentralkörpers 114 ausgeführt. Der Zentralkörper 114 ist als gestuftes Hülsenteil mittels einer Selbstverstemmung im Ventilträger 10 gehalten. Ein schräg zum Zentralkörper 114 im Ventilträger 10 verlaufender Druckmittelpfad 132 weist ein in Richtung der Radbremse 3 sperrendes Rückschlagventil 133 auf, das über einen zwischen dem Ventilträger 10 und dem Ventilaufnahmekörper 9 beabstandeten Ringfilter 22 so­ wie mittels wenigstens einem in der Abbildung erkennbaren Freigang am Plattenfilter 21 eine die Flüssigkeit filtrie­ rende Druckmittelverbindung zwischen der Radbremse 3 und dem Bremsdruckgeber 5 bzw. der Hilfsdruckpumpe 18 ermög­ licht.The space 117 is connected via a channel branch 129 , which extends between the central body 114 and the Ventilträ ger 10 , with a cross-sectional constriction 130 provided in the lower region of the central body 114 , which is preferably created by an aperture insert 131 . The extending with its extension into the interior of the valve rotationally symmetrical Zen tralkkörper 114 is pressed or caulked in the stepped bore of the valve carrier 10 . In the embodiment shown, the valve seat 116 is designed as an integral part of the bore of the central body 114 which extends coaxially with the valve closing member 11 . The central body 114 is held as a stepped sleeve part by means of a Selbstverstemmung in the valve support 10th A pressure medium path 132 , which runs obliquely to the central body 114 in the valve carrier 10 , has a check valve 133 which blocks in the direction of the wheel brake 3 and which is connected via a ring filter 22 spaced between the valve carrier 10 and the valve receiving body 9 and by means of at least one clearance on the plate filter 21 which can be seen in the illustration a fluid filtering fluid pressure connection between the wheel brake 3 and the brake pressure sensor 5 or the auxiliary pressure pump 18 enables light.

Die Fig. 2 zeigt abweichend von Fig. 1 eine spezielle Ausgestaltung der Kanalverengung 130 mittels eines Blenden­ einsatzes 131, der im wesentlichen die Kontur einer Düse aufweist und als dünnwandiger Formkörper, vergleichbar mit einem Venturirohr, gestaltet ist. Der Blendeneinsatz 131 weist einen mit Ausnehmungen 134 versehenen Bund 135 auf, der zwischen dem Plattenfilter 21 und dem Ventilträger 10 eingespannt ist. Die Ausnehmung 134 ist derart gestaltet, daß sie das Rückschlagventil 133 im Druckmittelpfad 132 teilweise überdeckt, um das Rückschlagventil 133 im Druck­ mittelpfad 132 zu halten. Der Blendeneinsatz 131 ist vor­ zugsweise als Dünnblech-Preßteil oder Kunststoff-Spritzguß­ teil ausgeführt. Die Kanalverengung ist einerseits inner­ halb des Blendeneinsatzes 131 als Kreisquerschnitt auf den Druckmittelstrom des Bremsdruckgebers 5 bzw. der Hilfs­ druckpumpe 18 wirksam, andererseits bewirkt die Ausformung des Blendeneinsatzes 131 als Düsenmundstück einen verjüng­ ten Ringquerschnitt im Bereich der Einmündung der Kanalab­ zweigung 129 in den Hauptstrom der Hauptdruckleitung 2. Fig. 2 is different from Fig. 1, a special configuration of the channel constriction 130 by means of a panel insert 131, which essentially has the contour of a nozzle and is designed as a thin-walled shaped bodies, similar to a venturi tube. The diaphragm insert 131 has a collar 135 , which is provided with recesses 134 and is clamped between the plate filter 21 and the valve carrier 10 . The recess 134 is designed such that it partially covers the check valve 133 in the pressurized medium path 132, fluid path to the check valve 133 in the pressure to keep the 132nd The panel insert 131 is preferably designed as a thin sheet metal part or plastic injection molding. The channel narrowing is effective within half of the orifice insert 131 as a circular cross-section on the pressure medium flow of the brake pressure transducer 5 or the auxiliary pressure pump 18 , on the other hand, the shape of the orifice insert 131 as a nozzle mouthpiece causes a tapered ring cross-section in the region of the junction of the duct branch 129 into the main flow of the Main pressure line 2 .

Alle aus der bildlichen Darstellung von Fig. 2 ersicht­ lichen weiteren Elemente entsprechen im wesentlichen dem Aufbau und der Funktion nach Fig. 1.All of the other elements shown in the pictorial representation of FIG. 2 essentially correspond to the structure and function of FIG. 1.

Nachfolgend wird die Funktionsweise der Erfindung erläutert:
Während einer nicht geregelten, schlupffreien Normalbrems­ phase befindet sich das Einlaßventil 1 in der elektromagne­ tisch nicht erregten, offenen Grundstellung. Bei einer Be­ tätigung des Bremsdruckgebers 5 wird ein steigender Druck­ aufbaugradient im Einlaßventil 1 initiiert, der in der Ka­ nalverengung 130 zu einer erheblich anwachsenden Strömungs­ geschwindigkeit führt, die in der im wesentlichen spaltför­ migen Kanalabzweigung 129 in Richtung des Zwischenraums 117 ein Druckgefälle einstellt. Dieses Druckgefälle ist auch über den Dichtring 124 am Ringkolben 8 wirksam. Durch die erhöhte Druckdifferenz zwischen den beiden Stirnflächen am Ringkolben 8 erhält die den Ringkolben 8 in Ruhestellung haltende Druckfeder 7 eine hydrodynamische Unterstützung, so daß auch in der schnellen Anbremsphase eine ungehinderte Druckmittelverbindung zwischen dem Dichtsitz 115 und der Stirnfläche des Reglerkolbens 8 besteht. Der Ringkolben 8 bleibt somit in der abbildungsgemäßen Ruhestellung an der Bohrungsstufe auf Anschlag, so daß der Bremsdruck sich un­ gehindert zur Radbremse 3 fortpflanzen kann. Die uner­ wünschte vorzeitige Aktivierung der im Ringkolben 8 inte­ grierten Blende 4 unterbleibt.The mode of operation of the invention is explained below:
During a non-regulated, slip-free normal braking phase, the inlet valve 1 is in the electromagnetically not excited, open basic position. When the brake pressure transducer 5 is actuated, a rising pressure build-up gradient is initiated in the inlet valve 1 , which leads to a considerably increasing flow velocity in the channel narrowing 130 , which sets a pressure drop in the essentially spalt-shaped channel branch 129 in the direction of the space 117 . This pressure drop is also effective via the sealing ring 124 on the annular piston 8 . Due to the increased pressure difference between the two end faces on the annular piston 8 , the compression spring 7 holding the annular piston 8 in the rest position receives hydrodynamic support, so that even in the rapid braking phase there is an unimpeded pressure medium connection between the sealing seat 115 and the end face of the regulator piston 8 . The annular piston 8 thus remains in the illustrated rest position at the bore step as far as it will go, so that the brake pressure can propagate unhindered to the wheel brake 3 . The unwanted premature activation of the 8 integrated diaphragm in the ring piston 4 is omitted.

Beim Lösen des Bremspedals wird der Bremsdruck in umgekehr­ ter Richtung über das offene Ventilschließglied 11 und über das Rückschlagventil 133 in Richtung des Bremsdruckgebers 5 wieder abgebaut.When the brake pedal is released, the brake pressure is reduced in the opposite direction via the open valve closing member 11 and the check valve 133 in the direction of the brake pressure transmitter 5 .

Überschreitet bei geschlossenem Einlaßventil während einer Bremsschlupfregelung die Druckdifferenz zwischen dem Ven­ tileinlaß (Hauptzylinder-/Pumpendruck) und Ventilausgang (Radbremsdruck) einen durch die Druckfeder 7 eingestellten Wert, so wird der Ringkolben 8 infolge der resultierenden Druckkraft am Dichtring 124 gegen die Federkraft verschoben und kommt am Magnetkern 127 dichtend zur Anlage. Eine Druckmittelverbindung zur Radbremse 3 besteht somit aus­ schließlich über die Blende 4 des Ringkolbens 8.When the inlet valve is closed during a brake slip control, the pressure difference between the valve inlet (master cylinder / pump pressure) and valve outlet (wheel brake pressure) exceeds a value set by the compression spring 7 , the annular piston 8 is displaced as a result of the resulting pressure force on the sealing ring 124 against the spring force and comes on the magnetic core 127 sealing to the system. A pressure medium connection to the wheel brake 3 thus finally consists of the orifice 4 of the annular piston 8 .

Öffnet das Einlaßventil 1 wieder seinen regulären Durchgang über das Ventilschließglied 11, so gelangt das nachströmen­ de Fluid von der im ABS-Betrieb befindlichen Hilfsdruckpum­ pe 18 ausschließlich über die Blende 4 im Ringkolben 8 zur Radbremse 3 und wird derart abgebremst, daß beim nachfol­ genden wiederholten Schließen des Einlaßventils 1 der Druckstoß und damit das Geräusch reduziert ist. Beim Unter­ schreiten der zur Betätigung des Ringkolbens 8 notwendigen Schaltdruckdifferenz sowie beim Unterbrechen des Bremsvor­ gangs gelangt der Ringkolben 8 wieder in die den Strömungs­ durchlaß vergrößernde Ausgangsstellung zurück. Opens the inlet valve 1 again its regular passage through the valve closing member 11 , the inflowing de fluid from the auxiliary pressure pump 18 in ABS operation passes exclusively via the orifice 4 in the annular piston 8 to the wheel brake 3 and is braked in such a way that repeated at the following Closing the inlet valve 1, the pressure surge and thus the noise is reduced. When under the switching pressure difference necessary to actuate the annular piston 8 and when interrupting the brake operation, the annular piston 8 returns to the flow-increasing initial position.

Zusammenfassend wird festgestellt, daß der Einfluß der Druckaufbaugeschwindigkeit bei manueller Bremsbetätigung durch die Erfindung vernachlässigbar gering ist, da zwangs­ läufig mit zunehmender Druckaufbaugeschwindigkeit das sich am Ringkolben einstellende Druckgefälle bzw. die Druckdif­ ferenz im verengten Strömungsquerschnitt und damit auch in der verengten Kanalabzweigung zunimmt, womit die schaltbare Blende in jedem Falle in der Normalbremsphase und damit bei geöffnetem Ventilschließglied wirkungslos verharrt. Damit kann auch der Umschaltdruck, bei dem der Ringkolben in der Bremsschlupfregelung aktiviert wird, erheblich gesenkt wer­ den, wodurch sich vorteilhaft auch die Volumenstromschwan­ kungen zum Zwecke einer guten Regelgüte während der Brems­ schlupfregelung gering halten lassen. Zwangsläufig vermin­ dern sich die Ventilgeräusche gegenüber den bisher vorge­ schlagenen Lösungen und der Druckaufbaugradient kann Wunsch oder Bedarf für den manuell gesteuerten, blockierfreien Bremsenbetrieb vergrößert werden.In summary it is stated that the influence of Pressure build-up speed with manual brake application is negligible by the invention, because compulsory commonly with increasing pressure build-up speed pressure drop or the pressure dif reference in the narrow flow cross section and thus also in the narrowed channel branch increases, making the switchable Aperture in any case in the normal braking phase and thus opened valve closing member remains ineffective. In order to can also the switching pressure at which the ring piston in the Brake slip control is activated, significantly reduced who the, which is also advantageous for the volume flow swan for good control quality during braking Keep the slip control low. Inevitably min the valve noise compared to the previously featured proposed solutions and the pressure build-up gradient can be desired or need for the manually controlled, non-blocking Brake operation can be increased.

BezugszeichenlisteReference list

1 Einlaßventil
2 Hauptdruckleitung
3 Radbremse
4 Blende
5 Bremsdruckgeber
7 Druckfeder
8 Ringkolben
9 Ventilaufnahmekörper
10 Ventilträger
11 Ventilschließglied
21 Plattenfilter
22 Ringfilter
114 Zentralkörper
115 Dichtsitz
116 Ventilsitz
117 Zwischenraum
124 Dichtring
126 Ringraum
127 Magnetkern
129 Kanalabzweigung
130 Kanalverengung
131 Blendeneinsatz
132 Druckmittelpfad
133 Rückschlagventil
134 Ausnehmung
135 Bund
136 Festblende 1 inlet valve
2 main pressure line
3 wheel brake
4 aperture
5 brake pressure sensors
7 compression spring
8 ring pistons
9 valve body
10 valve supports
11 valve closing member
21 plate filters
22 ring filter
114 central body
115 sealing seat
116 valve seat
117 space
124 sealing ring
126 annulus
127 magnetic core
129 channel branch
130 channel narrowing
131 aperture insert
132 pressure medium path
133 check valve
134 recess
135 fret
136 fixed aperture

Claims (10)

1. Elektromagnetventil, insbesondere für hydraulische Bremsanlagen mit Schlupfregelung, mit einem Ventilträ­ ger, der in einem Ringraum ein Ventilschließglied auf­ weist, das mit einem im Ventilträger angeordneten Ven­ tilsitz korrespondiert, mit einer schaltbaren Blende, die in einer ersten Schaltstellung einen ungehinderten hydraulischen Durchlaß im Elektromagnetventil herstellt und in einer weiteren Schaltstellung den Druckmittel­ durchlaß im Elektromagnetventil begrenzt, wobei die schaltbare Blende Bestandteil eines im Elektromagnetven­ til integrierten Ringkolbens ist, nach Patent . . . (Patentanmeldung Aktenzeichen P 43 19 227.0), dadurch gekennzeichnet, daß ein stromaufwärts zum Ventilsitz (116) angeordneter Druckmittelkanal eine Ka­ nalverengung (130) aufweist, in die ein bis in einen Zwischenraum (117) des Ringkolbens (8) sich erstreckende Kanalabzweigung (129) mit geringer Nennweite einmündet, so daß in der Kanalverengung (130) ein Teil der Druck­ energie einer Druckmittelsäule in kinetische Energie um­ gewandelt ist, die in der zur einen Stirnfläche des Ringkolbens (8) führenden Kanalabzweigung (129) ein Druckgefälle erzeugt.1. Solenoid valve, in particular for hydraulic brake systems with slip control, with a Ventilträ ger, which has a valve closing member in an annular space, which corresponds to a valve seat arranged in the valve carrier Ven, with a switchable orifice which, in a first switching position, has an unhindered hydraulic passage in Manufactures solenoid valve and limits the pressure medium passage in the solenoid valve in a further switching position, the switchable orifice being part of an annular piston integrated in the solenoid valve, according to the patent. . . (Patent application file number P 43 19 227.0), characterized in that a pressure medium channel arranged upstream of the valve seat ( 116 ) has a channel narrowing ( 130 ) into which a channel branch ( 129 ) extending into an intermediate space ( 117 ) of the annular piston ( 8 ) ) opens with a small nominal width, so that in the channel constriction ( 130 ) a part of the pressure energy of a pressure medium column is converted into kinetic energy, which produces a pressure drop in the channel branch ( 129 ) leading to one end face of the annular piston ( 8 ). 2. Elektromagnetventil nach Anspruch 1, dadurch ge­ kennzeichnet, daß der Ventilsitz (116) im hülsenförmigen Zentralkörper (114) angeordnet ist, der im Ventilträger (10) eingesetzt ist, und daß der Zen­ tralkörper (114) die Kanalverengung (130) aufnimmt. 2. Solenoid valve according to claim 1, characterized in that the valve seat ( 116 ) is arranged in the sleeve-shaped central body ( 114 ) which is inserted in the valve carrier ( 10 ), and that the Zen tralkkörper ( 114 ) receives the channel constriction ( 130 ). 3. Elektromagnetventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß zwischen dem Zentral­ körper (114) und dem Ventilträger (10) die Kanalabzwei­ gung, vorzugsweise in Form eines Druckmittelspaltes, ge­ führt ist, die in den von einer Stirnfläche des Ringkol­ bens (8) begrenzten Zwischenraum (117) einmündet.3. Solenoid valve according to claim 1 or 2, characterized in that between the central body ( 114 ) and the valve support ( 10 ), the Kanalabzwei supply, preferably in the form of a pressure medium gap, leads GE, which in the from an end face of the ring piston ( 8 ) limited space ( 117 ) opens out. 4. Elektromagnetventil nach mindestens einem der vorherge­ henden Ansprüche, dadurch gekennzeichnet, daß die der Kanalabzweigung (129) zugewandte Stirnfläche am Ringkolben (8) von einer Ringdichtung (124) im Zwischenraum (117) begrenzt ist.4. Solenoid valve according to at least one of the preceding claims, characterized in that the channel branch ( 129 ) facing the end face on the annular piston ( 8 ) by an annular seal ( 124 ) in the intermediate space ( 117 ) is limited. 5. Elektromagnetventil nach mindestens einem der vorherge­ henden Ansprüche 1 bis 4, dadurch gekenn­ zeichnet, daß die Kanalabzweigung (129) zwischen einer im Ventilträger (10) angeordneten Festblende (136) und der sich in den Zentralkörper (114) erstreckenden Kanalverengung (130) einmündet.5. Solenoid valve according to at least one of the preceding claims 1 to 4, characterized in that the channel branch ( 129 ) between a in the valve carrier ( 10 ) arranged fixed diaphragm ( 136 ) and the channel narrowing ( 130 ) extending into the central body ( 114 ) flows into. 6. Elektromagnetventil nach mindestens einem der vorherge­ henden Ansprüche, dadurch gekennzeichnet, daß die Kanalverengung (130) durch einen Blendeneinsatz (131) gebildet ist.6. Electromagnetic valve according to at least one of the preceding claims, characterized in that the channel constriction ( 130 ) is formed by an orifice insert ( 131 ). 7. Elektromagnetventil nach Anspruch 6, dadurch ge­ kennzeichnet, daß der Blendeneinsatz (131) aus einem im wesentlichen die Kontur einer Düse aufwei­ senden dünnwandigen Formkörper besteht, der vorzugsweise reibschlüssig im Ventilträger (10) befestigt ist.7. Solenoid valve according to claim 6, characterized in that the diaphragm insert ( 131 ) consists of a substantially the contour of a nozzle aufwei send thin-walled molded body, which is preferably frictionally attached in the valve carrier ( 10 ). 8. Elektromagnetventil nach Anspruch 6, dadurch ge­ kennzeichnet, daß der Blendeneinsatz (131) einen Bund (135) aufweist, der zwischen einen am Ventil­ träger (10) befestigten Plattenfilter (21) und dem Ven­ tilträger (10) eingespannt ist.8. Solenoid valve according to claim 6, characterized in that the diaphragm insert ( 131 ) has a collar ( 135 ) which is clamped between a valve carrier ( 10 ) attached plate filter ( 21 ) and the Ven tilträger ( 10 ). 9. Elektromagnetventil nach Anspruch 8, dadurch ge­ kennzeichnet, daß der Bund (135) wenigstens eine Ausnehmung (134) besitzt, die einen zum Ventil­ schließglied (11) parallel geschalteten Druckmittelpfad (132) freigibt.9. Solenoid valve according to claim 8, characterized in that the collar ( 135 ) has at least one recess ( 134 ), which releases a valve member ( 11 ) connected in parallel pressure medium path ( 132 ). 10. Elektromagnetventil nach Anspruch 9, dadurch ge­ kennzeichnet, daß der Bund (135) den Druck­ mittelpfad (132) teilweise überdeckt, in dem ein in Richtung des Bunds (135) öffnendes Rückschlagventil (133) eingesetzt ist.10. Solenoid valve as claimed in claim 9, characterized in that the collar (135) middle path the pressure (132) partially covered, in which an opening in the direction of the collar (135) check valve (133) is inserted.
DE4339305A 1993-06-09 1993-11-18 Solenoid valve for hydraulic brake system with feedback control Withdrawn DE4339305A1 (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
DE4339305A DE4339305A1 (en) 1993-06-09 1993-11-18 Solenoid valve for hydraulic brake system with feedback control
US08/464,902 US5647644A (en) 1993-11-18 1994-11-04 Solenoid valve, especially for hydraulic brake systems with slip control
DE59408551T DE59408551D1 (en) 1993-11-18 1994-11-04 ELECTROMAGNETIC VALVE, ESPECIALLY FOR HYDRAULIC BRAKE SYSTEMS WITH SLIP CONTROL
EP95900111A EP0728085B1 (en) 1993-11-18 1994-11-04 Solenoid valve for, in particular, hydraulic brake systems with slip control
ES95900111T ES2134428T3 (en) 1993-11-18 1994-11-04 ELECTROMAGNETIC VALVE, IN PARTICULAR FOR HYDRAULIC BRAKE EQUIPMENT WITH SLIDING REGULATION.
JP51418595A JP3735659B2 (en) 1993-11-18 1994-11-04 Solenoid valve, especially for hydraulic brake device with slip control device
CZ951816A CZ181695A3 (en) 1993-11-18 1994-11-04 Electromagnetic valve, particularly for hydraulic brake devices with slip control
SK966-95A SK96695A3 (en) 1993-11-18 1994-11-04 Solenoid valve for, in particular, hydraulic brake system with slip control
PCT/EP1994/003622 WO1995013945A1 (en) 1993-11-18 1994-11-04 Solenoid valve for, in particular, hydraulic brake systems with slip control
KR1019950702900A KR960700167A (en) 1993-06-09 1995-07-14 Solenoid valve for hydraulic braking system with slip control system (ELEKTROMAGNETVENTIL, INSBESONDERE FUR HYDRAULISCHE BREMSANLAGEN MIT SCHLUPFREGELUNG)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4319227A DE4319227A1 (en) 1993-06-09 1993-06-09 Hydraulic brake system with slip control
DE4339305A DE4339305A1 (en) 1993-06-09 1993-11-18 Solenoid valve for hydraulic brake system with feedback control

Publications (1)

Publication Number Publication Date
DE4339305A1 true DE4339305A1 (en) 1995-05-24

Family

ID=6490039

Family Applications (4)

Application Number Title Priority Date Filing Date
DE4319227A Withdrawn DE4319227A1 (en) 1993-06-09 1993-06-09 Hydraulic brake system with slip control
DE4339305A Withdrawn DE4339305A1 (en) 1993-06-09 1993-11-18 Solenoid valve for hydraulic brake system with feedback control
DE4403295A Withdrawn DE4403295A1 (en) 1993-06-09 1994-02-03 Vehicular hydraulic braking system with wheelslip control valves
DE59401774T Expired - Lifetime DE59401774D1 (en) 1993-06-09 1994-05-13 HYDRAULIC BRAKE SYSTEM WITH SLIP CONTROL

Family Applications Before (1)

Application Number Title Priority Date Filing Date
DE4319227A Withdrawn DE4319227A1 (en) 1993-06-09 1993-06-09 Hydraulic brake system with slip control

Family Applications After (2)

Application Number Title Priority Date Filing Date
DE4403295A Withdrawn DE4403295A1 (en) 1993-06-09 1994-02-03 Vehicular hydraulic braking system with wheelslip control valves
DE59401774T Expired - Lifetime DE59401774D1 (en) 1993-06-09 1994-05-13 HYDRAULIC BRAKE SYSTEM WITH SLIP CONTROL

Country Status (6)

Country Link
US (1) US5683150A (en)
EP (1) EP0700344B1 (en)
JP (1) JP3895367B2 (en)
KR (1) KR960700167A (en)
DE (4) DE4319227A1 (en)
WO (1) WO1994029150A1 (en)

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DE19711442A1 (en) * 1997-03-19 1998-09-24 Itt Mfg Enterprises Inc Solenoid inlet valve for motor vehicle hydraulic braking system
DE19727654A1 (en) * 1997-06-30 1999-01-07 Itt Mfg Enterprises Inc Hydraulic multi-stage valve operable by actuator
WO1999043523A1 (en) 1998-02-28 1999-09-02 Continental Teves Ag & Co. Ohg Electromagnetic valve
DE10114299A1 (en) * 2000-10-20 2002-05-29 Continental Teves Ag & Co Ohg Valve for regulated slip braking system controls liquid flow between first and second fluid connection, rate of flow through valve being regulated independently of its direction
DE19954616C2 (en) * 1998-11-13 2002-07-18 Mando Corp Solenoid valve for an anti-lock braking system
WO2003047934A1 (en) * 2001-11-30 2003-06-12 Robert Bosch Gmbh Hydraulic modulator for an anti-lock device and the production method of the same
WO2003053753A1 (en) 2001-12-08 2003-07-03 Continental Teves Ag & Co. Ohg Electromagnetic valve
DE10229789A1 (en) * 2002-02-02 2003-08-14 Continental Teves Ag & Co Ohg Electromagnetic valve for operating as a 2-way seat valve, has a cartridge-shaped valve casing with a magnetic armature opposite a magnetic core and a valve-closing element on a valve needle.
DE19607933B4 (en) * 1996-01-31 2005-12-22 Continental Teves Ag & Co. Ohg Solenoid valve
DE19635690B4 (en) * 1996-09-03 2006-07-06 Robert Bosch Gmbh Solenoid valve for a slip-controlled, hydraulic vehicle brake system
DE102008010007A1 (en) 2007-02-23 2008-08-28 Continental Teves Ag & Co. Ohg Dynamic pressure generating method for hydraulic wheel brake of motor vehicle, involves connecting brake circuit with actuating unit over separating valve that is closed by applying closing current
DE102008013353A1 (en) 2007-03-14 2008-10-16 Continental Teves Ag & Co. Ohg Dynamic pressure creating process for hydraulic brake involves setting separating valve control voltage, raising it above altered value and reducing control voltage

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US5887956A (en) * 1993-09-28 1999-03-30 Itt Automotive Europe Gmbh Hydraulic brake system with slip control
ES2134428T3 (en) * 1993-11-18 1999-10-01 Continental Teves Ag & Co Ohg ELECTROMAGNETIC VALVE, IN PARTICULAR FOR HYDRAULIC BRAKE EQUIPMENT WITH SLIDING REGULATION.
JPH09511468A (en) * 1994-02-03 1997-11-18 アイティーティー・オートモーティブ・ヨーロップ・ゲーエムベーハー Hydraulic brake device with slip control
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US5683150A (en) 1997-11-04
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DE4319227A1 (en) 1994-12-15
EP0700344B1 (en) 1997-02-05
EP0700344A1 (en) 1996-03-13
JP3895367B2 (en) 2007-03-22
KR960700167A (en) 1996-01-19
DE4403295A1 (en) 1995-08-17
WO1994029150A1 (en) 1994-12-22

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